US4056040A - Shock absorber - Google Patents

Shock absorber Download PDF

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Publication number
US4056040A
US4056040A US05/568,390 US56839075A US4056040A US 4056040 A US4056040 A US 4056040A US 56839075 A US56839075 A US 56839075A US 4056040 A US4056040 A US 4056040A
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Prior art keywords
shock absorber
main cylinder
cylinder
openings
piston
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Expired - Lifetime
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US05/568,390
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English (en)
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Hubert Fussangel
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Individual
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Priority claimed from DE2419118A external-priority patent/DE2419118A1/de
Priority claimed from DE19752506451 external-priority patent/DE2506451C2/de
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Priority to US05/832,815 priority Critical patent/US4151784A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/346—Throttling passages in the form of slots arranged in cylinder walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/224—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston which closes off fluid outlets in the cylinder bore by its own movement

Definitions

  • the shock absorbers comprise a cylinder containing a piston fixed to a piston rod and liquid acting on the piston, the cylinder having openings for the flow from it of the liquid upon movement of the piston and means for restricting the openings to provide the adjustment of the damping characteristic.
  • shock absorbers of this class are used in many fields of industry, for example in order to decelerate accelerated masses or to absorb shocks caused by the accelerated masses.
  • Typical applications for such shock absorbers are for example found in rolling mill and foundry machinery and equipment, conveying and lifting equipment, stamping machines, machine tools and construction machinery or the like, and also in heavy vehicles.
  • the shock absorbers are predominantly used wherever there is a need for accepting large loads at high speeds, in order to convert the resulting impact forces into smaller forces of longer duration and transmit the smaller forces to a machine body, foundation or the like.
  • power cylinders operated by hydraulic liquid under pressure are used.
  • Typical applications for such power cylinders are, for instance, in control and lifting jacks, and for raising, lowering or in other ways moving machine or vehicle components.
  • the aim of the present invention is to provide a shock absorber having an infinitely adjustable damping characteristic and comprising a cylinder containing a piston fixed to a piston rod and liquid acting on the piston, the cylinder having openings for the flow from it of the liquid upon movement of the piston and means for restricting the openings to provide the adjustment of the damping characteristic, which is especially suitable for industrial applications, which can be made in a space-saving manner and is of robust construction, which can be easily adjusted and which can also be adapted to provide it with a power cylinder capability.
  • the openings are provided in the peripheral wall of the cylinder and are axially spaced apart from each other in positions in which they are successively passed over and closed by the piston as it approaches the end of its stroke at one end and/or the other end of the cylinder.
  • the cylinder may be provided with an inlet for liquid under pressure to provide a single-acting power capability and the shock absorbing effect is either single-acting or double-acting.
  • shock absorber features and power cylinder features devices suitable for many different applications may be made and with these devices it is possible not only to control and drive machine and vehicle components in an optimum manner, but also to accelerate and/or decelerate them in a predetermined manner.
  • Shock absorbers in accordance with the invention may thus be made with a two-fold function, namely a power function and an accelerating and damping function.
  • the shock absorber can be adjusted to an optimum characteristic for each purpose, so that the resultant stressing of machine or vehicle components or other members to be moved can be kept within pre-determined values.
  • the linear movement control makes possible both a gentle transference of the mass in movement and the achievement of a uniform counter-pressure during the deceleration phase, and also a gentle transference of the arrested mass onto a fixed abutment. This contributes considerably to the preservation and increase in working life of machines and other devices, and also makes possible a considerable increase in the speed of movement for given stress values.
  • the shock absorber can also produce a considerable shortening of the time required for deceleration and thus a reduction of standstill time, loss of production and repair costs.
  • the shock absorber can be made single-acting or double-acting and may function solely as a shock absorber without a power function.
  • the axial spacing of the openings in the peripheral wall of the cylinder becomes progressively smaller towards one or both ends of the cylinder. This makes a low initial loading of the piston possible and subsequent increasing acceleration by adjustment of the other openings to larger cross-sections.
  • the full liquid pressure can be applied to the effective piston area.
  • the shock absorber can be made to operate as a normal power cylinder.
  • a desired gentle deceleration can then be ensured by progressive adjustment to decreasing cross-sections of the openings in the peripheral wall of the cylinder.
  • the restricting means may comprise an adjustment element movably mounted adjacent the outer ends of the openings.
  • the adjusting element may comprise diametrically opposed crescent-shaped segments.
  • the adjusting segments may be mounted on the inner face of an outer cylinder part which surrounds and is rotatably mounted on the cylinder. To adjust the damping characteristic it is then only necessary for the outer cylinder part together with the adjusting segments, to be rotated.
  • an adjusting cylinder may be used.
  • an outer cylinder part surrounds and is rotatably mounted on the cylinder and the outer cylinder part is provided with radial passages arranged to correspond in axial position to the openings through the peripheral wall of the cylinder, the outer cylinder part and the adjustment cylinder being rotationally fixed together.
  • the restricting means comprises an outer cylinder part surrounding and rotatably and eccentrically mounted on the cylinder.
  • the adjusting elements which are otherwise required for adjusting the damping characteristic in the form of separate components, such as the adjusting cylinder or the adjusting segments, can be completely omitted, since the adjustment of the damping characteristic is now directly obtained by utilising the eccentric arrangement of the outer cylinder part with respect to the cylinder.
  • shock absorbers in accordance with the invention are illustrated in the accompanying drawings, in which:
  • FIG. 1 is an axial section through a first example comprising a double-acting power cylinder which also constitutes a double-acting shock absorber;
  • FIG. 2 is a cross-section on the line II--II of FIG. 1;
  • FIG. 3 is a cross-section on the line III--III of FIG. 1;
  • FIG. 4 is an axial section through a second example comprising a power cylinder which has a piston rod and the piston rod end of which constitutes a shock absorber;
  • FIG. 5 is a cross-section on the line V--V of FIG. 4;
  • FIG. 6 is a cross-section on the line VI--VI of FIG. 4;
  • FIG. 7 is an axial section through a third example again comprising a power cylinder incorporating a shock absorber at one end;
  • FIG. 8 is a cross-section on the line VIII--VIII of FIG. 7;
  • FIG. 9 is a cross-section on the line IX--IX of FIG. 7;
  • FIG. 10 is an axial section through a fourth example comprising a double-acting power cylinder forming also a double-acting shock absorber;
  • FIG. 11 is a section on the line XI--XI in FIG. 10;
  • FIG. 12 is an axial section through a fifth example comprising a power cylinder with a shock absorber disposed at one end;
  • FIG. 12a is a section similar to FIG. 12 but showing a modification
  • FIG. 13 is an axial section through a sixth example comprising a power cylinder with a shock absorber disposed at one end;
  • FIG. 14 is an axial section through a seventh example comprising a power cylinder with a shock absorber disposed at one end;
  • FIG. 15 is a section on the line XV--XV of FIG. 14;
  • FIG. 16 shows a hydraulic control circuit for an example comprising a double-acting power cylinder forming also a double-acting shock absorber
  • FIG. 17 shows a hydraulic control circuit for a power cylinder forming a shock absorber at one end
  • FIG. 18 shows a hydraulic control circuit for a power cylinder forming a shock absorber at the other end.
  • a double-acting power cylinder 1 has screwed into it at one end a cylinder head 2, and at the other end a guide head 3.
  • the guide head 3 is secured axially by a securing disc 4.
  • a piston rod 5 is slidable in the guide head 3 and a piston 6 is axially slidable in the cylinder 1.
  • the piston rod 5 is fixed at its inner end by a nut 7 to the piston 6.
  • the end portions of the cylinder 1 are surrounded with a clearance, by outer cylinder parts 9 and 11, which are secured by retaining nuts 12 and 13 against axial movement.
  • the outer cylinder parts 9 and 11 are rotatably mounted directly upon the cylinder 1, and at their inward ends are mounted on the cylinder through the intermediary of bearing rings 14 and 15.
  • adjustment segments 21 and 22 In the vicinity of the passages 16 and 17 and disposed in diametrically opposite rows, are adjustment segments 21 and 22 which extend in annular spaces 18 and 19 between the outer cylinder parts 9 and 11 and the cylinder 1.
  • the adjustment segments 21, 22 are substantially sickle-shaped in cross-section and are disposed both in the retracted and in the extended range of the piston 6 in the cylinder 1. They are situated in pairs diametrically opposite each other (FIG. 2) and are fixed by screws 23 to the outer cylinder parts 9 and 11.
  • the radial distances between the inner faces of the adjustment segments and the radial passages 16 and 17 can be varied, thus enabling the desired shock absorber damping characteristic to be adjusted.
  • a hydraulic liquid inlet opening 24 which is in communication with the annular space 18.
  • the inlet opening 24 is also in communication, in a manner not shown, with a further feed opening 25, which is situated in the cylinder head 2 and is provided with a non-return valve the function of which is explained with reference to FIGS. 16 and 18.
  • the discharge opening 26 is in communication with the annular space 19.
  • a further hydraulic liquid feed opening 27 which also has a non-return valve which is subsequently described in more detail with reference to FIGS. 17 and 18.
  • the feed opening 27 is in communication, via a radial duct 28 in the working cylinder 1, with an axial duct 29 in the guide head 3.
  • the axial duct 29 leads into a pressure chamber 31 of the cylinder 1.
  • the mode of operation of the shock absorber illustrated in FIGS. 1 to 3 is as follows:
  • Pressurised liquid then immediately flows into the space behind the left-hand face of the piston 6 through those radial passages 16 which are situated furthest to the left, so that this piston is moved faster towards the right. Further pressurised liquid then flows in the same way through each of the radial passages 16, as they are uncovered, so that the piston rod 5 is extended with increasing speed as a consequence of the increasing flow of pressurised liquid.
  • the openings 32 of larger diameter have the function, after the piston 6 has moved through a predetermined distance, of applying the full liquid flow to the piston without any throttling effect.
  • the fluid expelled from the chamber 31 is conducted through the radial passages 17 and 33 and the annular chamber 19, into the discharge opening 26 and thence to a reservoir.
  • the feed opening 27 is fitted with a non-return valve, which is disposed outside the shock absorber and prevents an outward flow of the pressurised liquid.
  • the radial passages 17 are successively passed over by the piston 6, so that a progressive throttling effect is produced.
  • the deceleration thus produced can be regulated by suitable adjustment of the adjustment segments 22 provided at this end of the cylinder. It is thus possible to regulate both the acceleration and also the deceleration of the shock absorber in a linear manner.
  • the piston rod 5 can also be moved under power from its extended position into the retracted position. This is achieved initially by introducing liquid under pressure through the feed opening 27, whereby the liquid acts, via the radial duct 28 and the axial duct 29, upon the face at the piston rod end of the piston 6, so that the piston is moved by pressure away from its extended position.
  • a shock absorber constructed as a driving cylinder which makes possible both a linear deceleration and also linear acceleration and thereby ensures a progressive control.
  • the double-acting shock absorber can incorporate only a single-acting power cylinder.
  • the shock absorber then operates as a pushing or pulling power cylinder, depending upon whether the piston end face or piston rod end face of the piston 6 is subjected to pressurised liquid. If, for example, the piston rod end face is subjected to pressure, then the liquid on the other side of the piston flows out against no back pressure through the passages 16, the annular space 19 and the inlet opening 24 into a reservoir. As soon as the piston 6 has passed over the passages 16, an increasing back-pressure builds up in the decelerating movement of the piston and this pressure dies away again after the deceleration has been completed.
  • the above-described controlling of the shock absorber can also be effected inversely, by pressurising the piston end face with pressurised liquid and by using the piston rod end face of the piston, after the working range extending as far as the passages 17 has been passed, for the purpose of damping.
  • the pressurised liquid flows out into a reservoir through the passages 17, the annular space 19 and through the opening 26.
  • the opening 27 is closed by its non-return valve.
  • the shock absorber illustrated in FIGS. 1 to 3 can also be used without any power capability that is solely as a shock absorber, by supplying no pressurised liquid.
  • both the chambers at the piston end face and also the piston rod end face of the piston are in communication with each other through appropriate ducting and at a slight pressure with a tank, and both faces of the piston are substantially unpressurised.
  • the non-return valves already mentioned are associated with the two openings 25 and 27 and these valves make possible the forced circulation necessary for cooling the hydraulic liquid and permit the piston to be moved from each of the end positions without throttling.
  • FIGS. 1 to 3 when acting solely as a shock absorber is hydraulically connected as shown in FIG. 16.
  • the feed openings 25, 27 and the discharge openings 24, 26 are in communication via pipes 25a, 27a and 24a, 26a, with a liquid tank 30.
  • Non-return valves 24b, 25b, 26b, 27b, are provided in the pipes 24a, 25a, 26a, 27a.
  • the non-return valves 24b, 26b allow flow in the direction indicated by arrows adjacent the valves and the non-return valves 25b, 27b allow flow in the inlet direction also indicated by arrows near the valves. In this manner, the necessary forced circulation of the liquid is made possible.
  • FIGS. 4 to 6 is generally similar to the example shown in FIGS. 1 to 3, but with the difference that the damping passages are not situated at both ends of the cylinder, but only at the piston rod end.
  • This shock absorber with damping only at the piston rod end may act as either a double-acting power cylinder, as a single-acting power cylinder acting in either direction, or solely as a shock absorber with no power capability.
  • the hydraulic system for the case last described is illustrated in FIG. 17.
  • shock absorbers are frequently required in industry, for example in rolling mills, step-by-step transport devices are driven by two power cylinders situated one at each side of the transporting device. Since such devices operate at very high speeds, conventional limiting position dampers may become overloaded, and as a consequence of the high impacts and excessive stressing of the material, such devices frequently fail after a short period. This leads to very long standstill times and repair costs and also to an appreciable loss of production in the pull. These advantages are mitigated by using shock absorbers incorporating power cylinders in accordance with the invention.
  • the transporting device is provided at each side with a shock absorber with single-acting damping and a single-acting power capability.
  • the cylinders are so arranged in relationship to the transport device that the piston rods are both directed towards the transport device.
  • the damping part of the cylinder is also in each case at the end which is directed towards the transport device. If therefore, for example, the cylinder situated on the right-hand side of the transport device is pressurised with liquid and the transport device is thereby pulled towards the right, then the piston rod of the cylinder disposed on the left-hand side of the transport device is extended from its cylinder. During this movement, the piston of the left-hand shock absorber is pulled into the decelerating range of its movement and is then finally stopped. The reverse movement is then carried out by the cylinder situated at the left-hand side of the transport device, so that the deceleration then required is similarly effected by the shock absorber situated on the right-hand side of the transport device.
  • FIGS. 7 to 9 Another example of a shock absorber constructed in a similar manner to the example shown in FIGS. 4 to 6 is shown in FIGS. 7 to 9.
  • shock absorbers may for example be disposed one on each side of a transport device and have their piston rod ends directed towards the transport device.
  • the shock absorber end is disposed at that end of the cylinder which is remote from the transport device. If, for instance, the cylinder of the shock absorber on the right-hand side of the transport device is pressurised with liquid so that it pulls the transport device towards the right, then towards the end of its power stroke, its piston moves into the decelerating range so that the movement is retarded or damped.
  • the actuation of the shock absorber on the left-hand side of the transport device is carried out in a similar manner. Again as the piston approaches the end of its stroke, it is retarded.
  • a single-acting shock absorber not only to provide either a single-acting or double-acting power capability but also to connect the shock absorber in a hydraulic circuit in such a way that it acts only as a shock absorber.
  • the circuit for a shock absorber situated at the piston end of the cylinder is shown in FIG. 18.
  • pressurised liquid is conducted through the opening 24 and the pipe 24a into the liquid tank 30, while during the extension stroke, pressurised liquid passes out of the liquid tank 30 through the pipe 25a into the cylinder.
  • the necessary control of the flow of the pressurised liquid is effected by the appropriate construction of the non-return valves, in order firstly to produce the necessary liquid circulation for cooling the liquid and secondly to enable the piston to be moved out of its end positions by external forces.
  • the liquid tank 30 may be unpressurised or may be under some pressure produced by air or other gas, by elastic means or by a pump.
  • a particular example of use of a shock absorber in accordance with this invention is for the drive of a flying shears in a rolling mill, where it is necessary to provide a drive movement which is both impact-free and is also suitably accelerated and decelerated.
  • the shock absorbers incorporating power cylinders illustrated in FIGS. 10 to 13 are generally similar to the examples shown in FIGS. 1 to 9, but with the difference that no adjustment segments are provided for setting the shock absorber damping characteristic. Instead an eccentric and rotatable arrangement of the cylinder 1 with respect to the outer cylinder parts 9, 11 is utilised for this purpose.
  • an annular space 18, 19 is produced by the eccentric arrangement between each outer cylinder part 9, 11 and the cylinder 1, but as can be seen from FIG. 11, this is crescent-shaped.
  • pressurised liquid can flow out of the damping chamber 31 into the appropriate annular space 18 or 19 during the extension stroke and retracting stroke with a greater or lesser throttling effect to adjust the damping characteristic.
  • the outer cylinder parts 9, 11 can be secured in their adjusted rotational positions by nuts 12, 13.
  • FIG. 12a The example shown in FIG. 12a is modified in that the outer cylinder part 11 is journalled eccentrically not directly on the cylinder 1, but by means of eccentric support rings 15', 15". In the set rotational positions, the outer cylinder part 11 can be secured by a screw 15''' which is screwed into the supporting ring 15' and the inner end of which engages in an annular groove 15 IV in the cylinder 1.
  • shock absorbers illustrated in FIGS. 10 to 13, having a power capability and one or two shock absorber capabilities, make it possible, on account of the infinitely adjustable damping characteristic, to accelerate and/or decelerating the movement of the piston 6 linearly. Further, they are suitable on account of their robust construction for a large number of practical applications so that the loadings of machine or vehicle components or other moving parts can be maintained within predetermined values. The conservation resulting from this leads to a considerable increase in the working life of the machines or vehicles. An increase in the maximum speed of movement for a given loading is also possible. This leads to an appreciable shortening of the time required for deceleration and also to a reduction of standstill times, production losses and repair costs.
  • the example shown in FIGS. 14 and 15 comprises a power cylinder having a shock absorber at its piston end, and thus corresponds largely to the example shown in FIGS. 7 and 13.
  • the difference lies in the means for adjustment of the shock absorber characteristic. This is effected, in the example shown in FIGS. 14 and 15, by an adjustment cylinder 32 which is rotatably mounted directly upon the drive cylinder 1 and is rotationally fixed by a coupling bolt 33 to the outer cylinder part 9.
  • the outer cylinder part 9 can be fixed together with the adjustment cylinder 32, in an rotational position by a screw-threaded nut 12.
  • the damping chamber 31 is in communication with the annular chamber 18 via the passage 16, eccentrically disposed annular grooves 35 in the driving cylinder 1 and radial passages 36 in the adjustment cylinder 32.
  • the adjustment cylinder 32 can be rotated by means of the outer cylinder part 9 relative to the cylinder 1 in such a manner that the passage 16 and the passages 36 are nearly in register with one another as illustrated in FIG. 15.
  • the construction in accordance with the invention can also be applied to shock absorbers of lighter construction, especially those for automobiles, in which the outer cylinder part and the adjustment cylinder are together rotatably mounted on the lower end of the cylinder. It also of couse is possible to rotate the cylinder 1 and to hold the outer cylinder part and the adjustment cylinder stationary.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Damping Devices (AREA)
  • Actuator (AREA)
US05/568,390 1974-04-20 1975-04-16 Shock absorber Expired - Lifetime US4056040A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US05/832,815 US4151784A (en) 1974-04-20 1977-09-13 Shock absorber

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE2419118A DE2419118A1 (de) 1974-04-20 1974-04-20 Stufenlos verstellbarer stossdaempfer, insbesondere fuer industrielle anwendungszwecke
DT2419118 1974-04-20
DE19752506451 DE2506451C2 (de) 1975-02-15 1975-02-15 Stufenlos verstellbarer Stoßdämpfer, insbesondere für industrielle Anwendungszwecke
DT2506451 1975-02-15

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US05/832,815 Continuation-In-Part US4151784A (en) 1974-04-20 1977-09-13 Shock absorber

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US4056040A true US4056040A (en) 1977-11-01

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US05/568,390 Expired - Lifetime US4056040A (en) 1974-04-20 1975-04-16 Shock absorber

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US (1) US4056040A (nl)
JP (1) JPS50143984A (nl)
AT (1) AT351875B (nl)
CH (1) CH588646A5 (nl)
DD (1) DD119294A5 (nl)
FR (1) FR2268196B1 (nl)
GB (1) GB1499177A (nl)
IT (1) IT1035247B (nl)
NL (1) NL181134C (nl)
SE (1) SE423133B (nl)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4151784A (en) * 1974-04-20 1979-05-01 Hubert Fussangel Shock absorber
DE2805774A1 (de) * 1978-02-10 1979-08-16 Knorr Bremse Gmbh Daempfungssteuerungseinrichtung fuer den kolben eines arbeitszylinders
US4973854A (en) * 1987-11-28 1990-11-27 Herman Hemscheidt Maschinenfabrik Gmbh & Co. Hydraulic shock-absorber and vibration damper with adjustable damping
US5948021A (en) * 1998-02-24 1999-09-07 Hosmer-Dorrance Corporation Hydraulic cylinders for limb gait control
US6443271B2 (en) 2000-06-14 2002-09-03 Weforma Gmbh Shock absorber with cup-shaped stop cap
US20040163922A1 (en) * 2003-02-25 2004-08-26 Zf Sachs Ag Actuating device, in particular for a vehicle clutch
US20060249340A1 (en) * 2005-05-03 2006-11-09 Love Phillip W Impact dispersal device
US7270222B1 (en) * 2004-03-23 2007-09-18 Brandon Aymar Externally adjustable internal bypass shock absorber
EP1988296A1 (de) * 2007-05-02 2008-11-05 Siemens Aktiengesellschaft Variationen der Ventilschliessgeschwindigkeit durch Verwendung von unterschiedlichen Blenden
USRE40649E1 (en) 2001-09-13 2009-03-10 Arvinmeritor Technology, Llc Adjustable shock absorber
US20090120748A1 (en) * 2005-05-03 2009-05-14 Love Phillip W Variable Valve for Impact Dispersal Device
CN106763438A (zh) * 2017-02-03 2017-05-31 国网江苏省电力公司电力科学研究院 液压缓冲器
US20200191174A1 (en) * 2018-12-13 2020-06-18 Safran Landing Systems Canada Inc. Multi-channel hydraulic snubbing device
US10996016B1 (en) * 2019-08-22 2021-05-04 U.S. Government As Represented By The Secretary Of The Army Load distribution nut
CN114215818A (zh) * 2021-12-17 2022-03-22 张家港市友明机械制造有限公司 一种双头缓冲油压缸

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US2292336A (en) * 1939-12-15 1942-08-04 Hydraulic Dev Corp Inc Cushioning valve
US2443312A (en) * 1944-03-06 1948-06-15 Hpm Dev Corp Pressure cylinder
US3043277A (en) * 1960-07-20 1962-07-10 Carlson Martin Hydraulic door operator system and control means therefor
US3138066A (en) * 1961-10-27 1964-06-23 Phil Wood Ind Ltd Cushioned-stroke reciprocatory hydraulic motor
GB982003A (en) * 1962-06-02 1965-02-03 Frederick George Grisley Improvements in hydraulic or pneumatic programming apparatus
US3344894A (en) * 1965-10-14 1967-10-03 Rex Chainbelt Inc Adjustable hydraulic shock absorber
US3731770A (en) * 1971-05-19 1973-05-08 Ace Controls Adjustable shock absorber

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JPS4036417Y1 (nl) * 1964-10-31 1965-12-25

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2292336A (en) * 1939-12-15 1942-08-04 Hydraulic Dev Corp Inc Cushioning valve
US2443312A (en) * 1944-03-06 1948-06-15 Hpm Dev Corp Pressure cylinder
US3043277A (en) * 1960-07-20 1962-07-10 Carlson Martin Hydraulic door operator system and control means therefor
US3138066A (en) * 1961-10-27 1964-06-23 Phil Wood Ind Ltd Cushioned-stroke reciprocatory hydraulic motor
GB982003A (en) * 1962-06-02 1965-02-03 Frederick George Grisley Improvements in hydraulic or pneumatic programming apparatus
US3344894A (en) * 1965-10-14 1967-10-03 Rex Chainbelt Inc Adjustable hydraulic shock absorber
US3731770A (en) * 1971-05-19 1973-05-08 Ace Controls Adjustable shock absorber

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4151784A (en) * 1974-04-20 1979-05-01 Hubert Fussangel Shock absorber
DE2805774A1 (de) * 1978-02-10 1979-08-16 Knorr Bremse Gmbh Daempfungssteuerungseinrichtung fuer den kolben eines arbeitszylinders
US4973854A (en) * 1987-11-28 1990-11-27 Herman Hemscheidt Maschinenfabrik Gmbh & Co. Hydraulic shock-absorber and vibration damper with adjustable damping
US5948021A (en) * 1998-02-24 1999-09-07 Hosmer-Dorrance Corporation Hydraulic cylinders for limb gait control
US6443271B2 (en) 2000-06-14 2002-09-03 Weforma Gmbh Shock absorber with cup-shaped stop cap
USRE40649E1 (en) 2001-09-13 2009-03-10 Arvinmeritor Technology, Llc Adjustable shock absorber
US20040163922A1 (en) * 2003-02-25 2004-08-26 Zf Sachs Ag Actuating device, in particular for a vehicle clutch
US7270222B1 (en) * 2004-03-23 2007-09-18 Brandon Aymar Externally adjustable internal bypass shock absorber
US7472935B2 (en) 2005-05-03 2009-01-06 Phillip W Love Impact dispersal device
US20060249340A1 (en) * 2005-05-03 2006-11-09 Love Phillip W Impact dispersal device
US20090120748A1 (en) * 2005-05-03 2009-05-14 Love Phillip W Variable Valve for Impact Dispersal Device
US8020584B2 (en) 2005-05-03 2011-09-20 Love Phillip W Variable valve for impact dispersal device
US8424658B2 (en) 2005-05-03 2013-04-23 Phillip W. Love Pressure actuating valve for impact dispersal device
WO2008135328A1 (de) * 2007-05-02 2008-11-13 Siemens Aktiengesellschaft Variationen der ventilschliessgeschwindigkeit durch verwendung von unterschiedlichen blenden
EP1988296A1 (de) * 2007-05-02 2008-11-05 Siemens Aktiengesellschaft Variationen der Ventilschliessgeschwindigkeit durch Verwendung von unterschiedlichen Blenden
CN106763438A (zh) * 2017-02-03 2017-05-31 国网江苏省电力公司电力科学研究院 液压缓冲器
US20200191174A1 (en) * 2018-12-13 2020-06-18 Safran Landing Systems Canada Inc. Multi-channel hydraulic snubbing device
US10996016B1 (en) * 2019-08-22 2021-05-04 U.S. Government As Represented By The Secretary Of The Army Load distribution nut
CN114215818A (zh) * 2021-12-17 2022-03-22 张家港市友明机械制造有限公司 一种双头缓冲油压缸
CN114215818B (zh) * 2021-12-17 2023-10-31 张家港市友明机械制造有限公司 一种双头缓冲油压缸

Also Published As

Publication number Publication date
JPS50143984A (nl) 1975-11-19
SE7504454L (sv) 1975-10-21
FR2268196A1 (nl) 1975-11-14
NL7504646A (nl) 1975-10-22
NL181134B (nl) 1987-01-16
AT351875B (de) 1979-08-27
CH588646A5 (nl) 1977-06-15
DD119294A5 (nl) 1976-04-12
ATA298875A (de) 1979-01-15
FR2268196B1 (nl) 1981-07-24
NL181134C (nl) 1987-06-16
GB1499177A (en) 1978-01-25
IT1035247B (it) 1979-10-20
SE423133B (sv) 1982-04-13

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